US6216838B1 - Torque damper and damping device equipped with such a torque damper - Google Patents

Torque damper and damping device equipped with such a torque damper Download PDF

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Publication number
US6216838B1
US6216838B1 US09/125,697 US12569799A US6216838B1 US 6216838 B1 US6216838 B1 US 6216838B1 US 12569799 A US12569799 A US 12569799A US 6216838 B1 US6216838 B1 US 6216838B1
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United States
Prior art keywords
windows
guide washers
elements
disc
input
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Expired - Lifetime
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US09/125,697
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English (en)
Inventor
Michel Bacher
Josip Kovac
Patrick Lucsak
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Valeo SE
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Valeo SE
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Assigned to VALEO reassignment VALEO ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LUCSAK, PATRICK, BACHER, MICHEL, KOVAK, JOSIP
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12313—Wound springs characterised by the dimension or shape of spring-containing windows

Definitions

  • the present invention concerns torsion dampers and damping devices equipped with such torsion dampers, such as for example the devices which are incorporated in clutch friction members for motor vehicles.
  • Clutch friction members are known, equipped with a torsion damping device comprising two torsion dampers: a main damper and a predamper.
  • the main damper has an input element fixed to two guide washers disposed on each side of a disc.
  • the guide washers are connected together by struts, which fix them to each other.
  • the input element consists, in the case of an application to a clutch friction member, of a support disc on each face of which friction linings are fixed, intended to be clamped between the thrust and reaction plates of the clutch.
  • the input element can consist of a disc fixed directly to the vehicle engine flywheel; this can also be one of the guide washers which is extended radially and fixed directly to the engine flywheel.
  • the input element when it is a case of a friction lining support disc, is pressed against one of the guide washers of the main damper whilst being fixed thereto by the struts or, as a variant, by specific rivets.
  • the struts pass through scallops formed at the external periphery of the disc; in this case, the angular movement between the disc and guide washers is limited through the cooperation of the struts with the edge of the scallops.
  • this limitation is achieved by the fact that the helical springs constituting circumferentially acting elastic members, here with high stiffness, elastically coupling the guidance washers and the disc, come to have contiguous turns.
  • the guide washers surround the output element of the damper device consisting in general of an internally fluted hub; the same applies to the disc of the main damper, which for its part meshes with clearance with the hub.
  • the main damper is therefore kinematically driven directly by the input element.
  • the predamper is located between the disc and one of the guide washers of the main damper, and this radially below the springs of the main damper.
  • the predamper is placed kinematically directly upstream of the output element and also has two guide washers disposed on each side of a disc fixed with respect to rotation to the hub by means of teeth.
  • Elastic members such as helical springs, elastically couple the disc of the predamper to its associated guide washers.
  • This predamper disc is crimped to the hub, whose flutes have a different height in order to form a shoulder serving to fix the said disc axially.
  • the guide washers of the predamper are connected with respect to rotation to the disc of the main damper.
  • the circumferentially acting springs of the predamper are less stiff than the circumferentially acting springs of the main damper.
  • the predamper is adapted to filter the vibrations in the idling range of the engine, whilst the main damper is adapted to filter the vibrations in the normal operating range of the vehicle, referred to as the running range, as from the idling range of the engine; the predamper can also be adapted to filter the vibrations in the running range at low engine torque.
  • the elastic members are helical springs disposed in windows formed in the guide washers and the disc, respectively.
  • the three windows receiving one and the same spring namely the two windows in the guide washers and the window in the disc, are in line with each other; each of these windows has an internal edge, two lateral or support edges, and an external edge; as shown schematically in FIGS.
  • the windows 11 in the disc 1 and the windows 12 and 13 in the guide washers 2 and 3 respectively have an internal edge 14 and 114 and lateral edges 15 , 16 and 115 , 116 disposed along the three sides of a rectangle, the internal edge 14 or 114 extending along the length of the said rectangle; the external edge 17 , 117 which faces the internal edge 14 , 114 is curvilinear in shape with its concavity directed towards the internal edge 14 , 114 , in other words towards the axis 90 about which the disc 1 and guide washers 2 and 3 rotate in operation.
  • the external edge 117 and the internal edge 114 of the windows in the guide washers have been illustrated by a line representing the projection along the axis 90 , in the plane of the figure, of the generator which guides the helical spring 20 radially; in order to facilitate reading of the drawing, the window in the disc 11 is in solid lines, the dotted lines designating a window formed in the guide washers.
  • the helical spring 20 is a conventional spring whose axis 21 is rectilinear; when the spring 20 is placed in the windows 11 , 12 and 13 , its axis 21 is parallel to the internal edge 14 , 114 of the said windows and its end turns are in abutment on the lateral edges 15 , 115 and 16 , 116 of the said windows.
  • the above arrangement has the drawback that, in operation, whilst the torque transmitted by the springs 20 is still weak or nil, the spring 20 subjected to the action of the centrifugal force has a tendency to be progressively, with the speed, pressed against the external edge of the windows in the guide washers and/or in the disc whilst at the same time it deforms so that its axis 21 , initially rectilinear, adopts a curved shape whose concavity is turned towards the inside.
  • FIGS. 1 and 2 show the most usual embodiment in which the guidance role of the springs 20 is entrusted entirely to the guide washers 2 and 3 ; this is because, as can be seen in the figures, the end turns of the springs 20 in abutment on the lateral edges 115 , 116 are centred by the internal 114 and external 117 edges at their junction with the lateral edges 115 , 116 respectively; the flaps 18 , 19 , and therefore the external edge 117 , are semi-circular: the external edge 117 is an arc of a circle centred at 91 which is further towards the outside with respect to the axis 90 ; consequently, the external edge 17 of the window 11 in the disc 1 is an arc of a circle centred at 92 , further towards the outside compared with the point 91 ; the external edge 17 is consequently
  • the spring 20 adopts, initially, with a nil or very small transmitted torque, with the engine rotating at a sufficiently high speed, idling for example, a configuration as explained above and illustrated by FIG. 3, in which it is pressed against the external edge 117 of the windows 12 and 13 , its axis 21 becoming curved and the internal part of the end turns leaving the lateral support edges of the windows; when the speed increases still further, the phenomenon is accentuated as shown in FIG. 4, the end turns moving away from the lateral edges; when the disc 1 is moved with respect to the guide washers 2 and 3 , it is the external edge 17 of its windows 11 which initially comes into contact with the end turn of the spring 20 , as illustrated in FIG.
  • a torsion damper disposed between two rotating elements, an input element and an output element, and having circumferentially acting elastic members, two guide washers associated with one of the elements and disposed axially on each side of a disc associated with the other one of the elements, the circumferentially acting elastic members having an axis and acting between the two guide washers and the disc whilst being placed in windows placed opposite each other and formed in the guide washers and in the disc, the said windows having two lateral edges on which the ends of the elastic members are adapted to be in abutment, the windows having an external edge, the external edge of the windows formed in one of the guide washers having a portion offset internally, that is to say radially towards the rotation axis of the input and output elements, in an area which is not swept by the ends of the elastic members during the relative rotational movement, in one direction or the other, of the input and output elements; as provided for in this document, the offset portion, seen
  • the object of the present invention is to avoid these drawbacks.
  • a torsion damper of the above type is characterised by the fact that the windows in the two guide washers have an external edge having an internally offset portion, which extends circumferentially in the shape of an arc of a circle whose centre is situated towards the outside with respect to the rotation axis of the input and output elements.
  • the said external edge is connected to the lateral edges by connecting portions in the shape of an arc of a circle centred on the rotation axis of the input and output elements; between the internally offset portion on the one hand and each of the connecting portions on the other hand, the external edge has clearance portions offset radially towards the outside.
  • the clearance portions are arcs of a circle belonging to the same circle with the same centre as that which defines the internally offset portion.
  • the said external edge is the external edge of the windows formed in the guide washers.
  • the elastic members are helical springs coiled around their axis.
  • the damper according to the invention is well suited to an application to a motor vehicle: the input element is intended to be fixed or fixable to the vehicle engine flywheel, the output element being intended to be connected to the input to the vehicle gearbox.
  • Another object of the invention is a damping device comprising on the one hand a main damper kinematically acted on directly by the input element and on the other hand a predamper placed directly upstream of the output element, in which the main damper is a torsion damper as above.
  • FIGS. 1 to 5 are explanatory diagrams relating to the prior art already commented on above;
  • FIG. 6 is a view in section of a clutch friction disc having a damper according to the invention.
  • FIG. 7 is a partial side view of the disc of FIG. 6, to a smaller scale
  • FIG. 8 is a diagram showing a window in plan view according to the invention.
  • a main damper 50 can be seen, having an input element 51 here fixed to guide washers 52 , 53 disposed on each side of a disc 54 .
  • the guide washers 52 , 53 are connected together by struts 57 which fix them together.
  • Circumferentially acting elastic members 60 here helical springs, elastically couple the disc 54 to the guide washers 52 , 53 .
  • the input element 51 consists, in this application to a clutch friction member, of a support disc 55 on each of the faces of which friction linings 56 are fixed, intended to be clamped between the thrust and reaction plates of the clutch.
  • the friction lining support disc 55 is pressed against one of the guide washers 52 of the main damper 50 whilst being fixed to it by the struts 57 .
  • the struts 57 pass through scallops 58 formed at the periphery of the disc 54 ; the angular movement between the disc 54 and guide washers 52 and 53 is limited through the cooperation of the struts 57 with the edge of the scallops 58 .
  • the guide washers 52 and 53 surround the output element 61 of the damping device consisting of an internally fluted hub at 62 ; the same applies to the disc 54 of the main damper 50 , which for its part meshes with clearance with external flutes 63 on the hub 61 having a portion 64 of reduced height at one of its ends.
  • the predamper 80 is located between the disc 54 and one of the guide washers, here the washer 52 , of the main damper 50 , and this radially below the springs 60 of the said main damper 50 .
  • the predamper 80 also has two guide washers 82 , 83 disposed on each side of a disc 84 fixed with respect to rotation to the portion 64 of the flutes 63 on the hub 61 .
  • Circumferentially acting elastic members 85 here helical springs, elastically couple the guide washers 82 , 83 to the disc 84 .
  • This disc 84 of the predamper 80 is crimped to the hub 61 .
  • the springs 85 of the predamper 80 are less stiff than the springs 80 of the main damper 50 .
  • the predamper 80 is adapted to filter the vibrations notably in the idling range of the engine, whilst the main damper 50 is adapted to filter the vibrations in the normal operating range of the vehicle, referred to as the running range.
  • Each of the dampers 50 , 80 has a specific axially acting friction device 59 , 86 , in a manner known per se.
  • the springs 60 of the main damper are placed in windows placed opposite each other formed in the guide washers 52 , 53 and in the disc 54 . In order not to complicate the drawing, and to facilitate the explanation, these windows have been superimposed in the diagram in the diagram in FIG. 7 .
  • the windows 64 , 65 are formed in the guide washers 52 , 53 , and the window 66 in the disc 54 . These windows have internal 74 and external 77 edges, and lateral edges 75 and 76 serving as an abutment for the springs 60 ; according to the invention, the external edge 77 of the windows 64 , 65 formed in the guide washers 52 , 53 has a portion A which is offset internally, that is to say radially towards the rotation axis 90 of the input 51 and output 61 elements.
  • This radial offset is such that the portion A is as close as possible to the external contour of the spring 60 ; as will easily be understood, this portion A makes it possible to limit considerably the deformation of the spring 60 under the effect of centrifugal force; this portion A extends circumferentially in an area 93 which is not swept by the end turns of the spring 60 during the relative movement of the input 51 and output 61 elements, this being valid in one direction or the other, that is to say in the driving direction where the engine of the vehicle drives the wheels thereof and which corresponds to a movement of the windows in the disc in the clockwise direction about the axis 90 , as seen in FIG.
  • the invention also makes provision for connecting the external edge 77 to the lateral edges 75 , 76 by means of the portions B and C in the shape of an arc of a circle whose centre is merged with the rotation axis 90 of the input 51 and output 61 elements: by virtue of this arrangement, the end turns will, in spite of the centrifugal effect, always remain maintained in the angle formed by the lateral edges 75 , 76 and the portions B and C, and, during the angular movement, the action on the springs by the disc will always take place through the lateral edges of the windows in the disc, that is to say without parasitic friction, the external edge of the windows in the disc being free with respect to the portions B and C.
  • the portions A on the one hand and B and C on the other hand are separated by clearance portions D, D 2 , that is to say ones offset radially towards the outside with respect to them.
  • the internally offset portion A is in the shape of an arc of a circle whose centre 100 is situated towards the outside with respect to the axis 90 ; for the same reason, the clearance portions D, D 2 are also arcs of a circle belonging to the same circle which defines the internally offset portion A.
  • Connecting portions E of roughly radial orientation, connect the internally offset portion A to each of the clearance portions D and D 2 .
  • the circumferentially acting elastic means can consist, in each group of windows, of a single helical spring, or two concentric helical springs, as shown in FIG. 6 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
US09/125,697 1996-12-23 1997-12-22 Torque damper and damping device equipped with such a torque damper Expired - Lifetime US6216838B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9615864 1996-12-23
FR9615864A FR2757587B1 (fr) 1996-12-23 1996-12-23 Amortisseur de torsion perfectionne et dispositif amortisseur equipe d'un tel amortisseur de torsion
PCT/FR1997/002385 WO1998028554A1 (fr) 1996-12-23 1997-12-22 Amortisseur de torsion perfectionne et dispositif amortisseur equipe d'un tel amortisseur de torsion

Publications (1)

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US6216838B1 true US6216838B1 (en) 2001-04-17

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US09/125,697 Expired - Lifetime US6216838B1 (en) 1996-12-23 1997-12-22 Torque damper and damping device equipped with such a torque damper

Country Status (9)

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US (1) US6216838B1 (ko)
EP (1) EP0883757B1 (ko)
JP (1) JP4049401B2 (ko)
KR (1) KR100516572B1 (ko)
BR (1) BR9707596A (ko)
DE (1) DE19781599B4 (ko)
ES (1) ES2178035T3 (ko)
FR (1) FR2757587B1 (ko)
WO (1) WO1998028554A1 (ko)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060104608A1 (en) * 2004-11-12 2006-05-18 Joan Llach Film grain simulation for normal play and trick mode play for video playback systems
US20060115175A1 (en) * 2004-11-22 2006-06-01 Cooper Jeffrey A Methods, apparatus and system for film grain cache splitting for film grain simulation
US20080152250A1 (en) * 2004-11-23 2008-06-26 Cristina Gomila Low-Complexity Film Grain Simulation Technique
US20100080455A1 (en) * 2004-10-18 2010-04-01 Thomson Licensing Film grain simulation method
US20140318917A1 (en) * 2009-12-25 2014-10-30 Exedy Corporation Clutch device
US9098916B2 (en) 2004-11-17 2015-08-04 Thomson Licensing Bit-accurate film grain simulation method based on pre-computed transformed coefficients
US9117261B2 (en) 2004-11-16 2015-08-25 Thomson Licensing Film grain SEI message insertion for bit-accurate simulation in a video system
US9177364B2 (en) 2004-11-16 2015-11-03 Thomson Licensing Film grain simulation method based on pre-computed transform coefficients
US10715834B2 (en) 2007-05-10 2020-07-14 Interdigital Vc Holdings, Inc. Film grain simulation based on pre-computed transform coefficients
US20200386275A1 (en) * 2018-02-20 2020-12-10 Unipres Corporation Torsional vibration reduction apparatus

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3848508B2 (ja) * 1999-07-19 2006-11-22 株式会社エクセディ ダンパー機構
JP2007120589A (ja) * 2005-10-27 2007-05-17 Valeo Unisia Transmission Kk 捩り振動低減装置
JP5187104B2 (ja) * 2008-09-30 2013-04-24 アイシン精機株式会社 ダンパ装置
FR3052834B1 (fr) * 2016-06-16 2018-06-08 Valeo Embrayages Dispositif d'amortissement pour embrayage de vehicule automobile et embrayage comprenant un tel dispositif

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB100615A (en) 1916-02-29 1916-06-15 Napier & Son Ltd Improvements in or relating to Clutches.
US4240532A (en) 1978-09-21 1980-12-23 Chrysler Corporation Torsional isolator for torque converter lock-up mechanism
GB2167525A (en) 1984-11-22 1986-05-29 Fichtel & Sachs Ag A clutch disc arrangement
FR2609771A1 (fr) 1987-01-19 1988-07-22 Valeo Ensemble de verrouillage pour appareil hydrocinetique et appareil hydrocinetique comportant un tel ensemble de verrouillage, notamment pour vehicule automobile
DE4327574A1 (de) 1992-10-09 1994-04-14 Fichtel & Sachs Ag Torsionsdämpferscheibe
DE19536513A1 (de) 1994-09-29 1996-04-04 Exedy Corp Schwingungsdämpfer für eine Scheibenkupplung
EP0756105A1 (en) 1995-07-24 1997-01-29 Exedy Corporation Plate member for a damper disc assembly
US5651442A (en) * 1994-08-24 1997-07-29 Exedy Corporation Clutch disc subassembly, manufacturing method and jig for assembling the subassembly
US5762558A (en) * 1996-02-16 1998-06-09 Exedy Corporation Damper disc assemby and balance weight therefor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2652399B1 (fr) * 1989-09-26 1994-06-24 Valeo Dispositif amortisseur de torsion a patins de frottement, notamment pour vehicule automobile.
US5052664A (en) * 1989-11-01 1991-10-01 Barnes Group Inc. Arcuate spring
FR2714436B1 (fr) * 1993-11-04 1996-05-31 Valeo Amortisseur de torsion, notamment friction d'embrayage pour véhicule automobile.
DE19636201C2 (de) * 1996-08-05 2000-04-06 Mannesmann Sachs Ag Torsionsschwingungsdämpfer

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB100615A (en) 1916-02-29 1916-06-15 Napier & Son Ltd Improvements in or relating to Clutches.
US4240532A (en) 1978-09-21 1980-12-23 Chrysler Corporation Torsional isolator for torque converter lock-up mechanism
GB2167525A (en) 1984-11-22 1986-05-29 Fichtel & Sachs Ag A clutch disc arrangement
FR2609771A1 (fr) 1987-01-19 1988-07-22 Valeo Ensemble de verrouillage pour appareil hydrocinetique et appareil hydrocinetique comportant un tel ensemble de verrouillage, notamment pour vehicule automobile
DE4327574A1 (de) 1992-10-09 1994-04-14 Fichtel & Sachs Ag Torsionsdämpferscheibe
US5651442A (en) * 1994-08-24 1997-07-29 Exedy Corporation Clutch disc subassembly, manufacturing method and jig for assembling the subassembly
DE19536513A1 (de) 1994-09-29 1996-04-04 Exedy Corp Schwingungsdämpfer für eine Scheibenkupplung
EP0756105A1 (en) 1995-07-24 1997-01-29 Exedy Corporation Plate member for a damper disc assembly
US5762558A (en) * 1996-02-16 1998-06-09 Exedy Corporation Damper disc assemby and balance weight therefor

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100080455A1 (en) * 2004-10-18 2010-04-01 Thomson Licensing Film grain simulation method
US8447127B2 (en) 2004-10-18 2013-05-21 Thomson Licensing Film grain simulation method
US8447124B2 (en) 2004-11-12 2013-05-21 Thomson Licensing Film grain simulation for normal play and trick mode play for video playback systems
US20060104608A1 (en) * 2004-11-12 2006-05-18 Joan Llach Film grain simulation for normal play and trick mode play for video playback systems
US9117261B2 (en) 2004-11-16 2015-08-25 Thomson Licensing Film grain SEI message insertion for bit-accurate simulation in a video system
US9177364B2 (en) 2004-11-16 2015-11-03 Thomson Licensing Film grain simulation method based on pre-computed transform coefficients
US9098916B2 (en) 2004-11-17 2015-08-04 Thomson Licensing Bit-accurate film grain simulation method based on pre-computed transformed coefficients
US20060115175A1 (en) * 2004-11-22 2006-06-01 Cooper Jeffrey A Methods, apparatus and system for film grain cache splitting for film grain simulation
US8483288B2 (en) 2004-11-22 2013-07-09 Thomson Licensing Methods, apparatus and system for film grain cache splitting for film grain simulation
US20080152250A1 (en) * 2004-11-23 2008-06-26 Cristina Gomila Low-Complexity Film Grain Simulation Technique
US8472526B2 (en) 2004-11-23 2013-06-25 Thomson Licensing Low-complexity film grain simulation technique
US10715834B2 (en) 2007-05-10 2020-07-14 Interdigital Vc Holdings, Inc. Film grain simulation based on pre-computed transform coefficients
US20140318917A1 (en) * 2009-12-25 2014-10-30 Exedy Corporation Clutch device
US9194441B2 (en) 2009-12-25 2015-11-24 Exedy Corporation Clutch device
US20200386275A1 (en) * 2018-02-20 2020-12-10 Unipres Corporation Torsional vibration reduction apparatus
US11754124B2 (en) * 2018-02-20 2023-09-12 Unipres Corporation Torsional vibration reduction apparatus

Also Published As

Publication number Publication date
BR9707596A (pt) 1999-07-27
KR19990087173A (ko) 1999-12-15
ES2178035T3 (es) 2002-12-16
FR2757587A1 (fr) 1998-06-26
EP0883757A1 (fr) 1998-12-16
WO1998028554A1 (fr) 1998-07-02
JP4049401B2 (ja) 2008-02-20
DE19781599B4 (de) 2007-09-06
JP2001510537A (ja) 2001-07-31
FR2757587B1 (fr) 1999-02-26
KR100516572B1 (ko) 2005-11-25
DE19781599T1 (de) 1999-04-15
EP0883757B1 (fr) 2002-07-17

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